Tabulating machine



Jan. 2, 1940. J. 'r. FERRY 2,185,841

TABULATING MACHINE Filed Dec. 24, 1936 15 Sheets-Sheet l INVENTOR. JOHN T. FERRY Jan. 2,' 1940. J. T. FERRY 2,185,341

TABULATING MACHINE Filed Dec. 24, 1936 15 Sheets-Sheet 2 INVENTOR. JOHN- T. FERRY A TORNEY Jan. 2,1940. T. FERRY I TABULATING MACHINE Filed Dec. 24, 1956 15 Sheets-Sheet 3 IN VEN TOR JOHN T. FERRY KW ATTORNEY Jan. 2, 1940. J. T. FERRY 2,185,841

TABULATING MACHINE Filed Dec. 24, 1936 15 Shets-Sheet 4 INVENTOR.

JOHN T.FERRY Jan. 2, 1940. J. T. FERRY TABULATING MACHINE 7 Filed Deb. 24, 1 9 36 l5 Sheets-Sheet INVENTOR JOHN T.FERRY AT TORNEY Jan. 2,1940. I J. T. FERRY v 2,185,841

TABULATING MACHINE Filed Dec. 24, 1936 15 Sheets-Sheet 7' FIGS.

' INVENTOR F|G.7. F IG.& JOHN T. FERRY BY a TTORNFY Jan. 2, 1940. J. T. FERRY TABULATING MACHINE Filed Deci 24, 1936 lS SheetS-Sheet B F'IG.|2.

INVENTOR F|G.l l. JOHN T.FERRY TORNEY Jan. 2, 1940. J. T. FERRY 2,185,841

TABULATING MACHINE Filed Dec. 24, 1936 15 Sheets-Sheet 9 INVENTOR JOHNT. FERRY ATTORNEY Fomzifr Eu .5

Jan. 2, 1940. J. T. FERRY iABULA'IING MACHINE Filed Dec. 24, 1936 15 Sheets-Sheet l0 II! llllll INVENTCR JOHN T.'FERRY BY ATTORNEY Jan. 2, 1940. J. FERRY 2,185,841

TABULATING MACHINE Filed Dec. 24, 1936 15 Sheets-Sheet 11 FIG. l7.

INVENTOR JOHN T. FERRY ATTORNEY Jan. 2, 1940. .1. T. FERRY TABULATING MACHINE Filed Dec. 24, 1936 15 Sheets-Sheet l2 FIG.2I.

FIG.|9.

v FIG 20.

INVENTOR JOHN T.FERRY BY ATTORNEY Jan. 2, 1940. J. T. FERRY 2,185,841

TABULATING MACHINE Filed Dec. 24, 1956 15 Sheets-Sheet l5 'OOOOOO' -OOOOOO 'OOOOOOO -OOOOOO -OOOOOOO OOOOOOO -OOOOOOO 'OOOOOOO -OOOOOOO OOOOOO OO OOO OOOOO INVENTOR JOHN T. F ERRY ATT RNEY Jan. 2, 1940. J; FERRY 2,185,841

TABULATING MACHINE Filed Dec. 24, 1936 15 Sheets-Sheet l4 FIG.28.

INVENTOR JOHN T. FERRY AT ORNEY 1940- J. T. FERRY TABULATING MACHINE Filed Dec. 24, 1936 15 Sheets-Sheet 15 u m w IIEIEEXWM INVENTOR JOHN T.FERRY AT RNEY Patented Jan. 2, 1940 PATENT OFFICE TABULATING MACHINE John T. Ferry, Ilion, N. Y., assignor to Remington Rand Inc., Buffalo, N. Y., a corporation of Delaware Application December 24, 1936, .Serial No. 117,552

11 Claims.

This invention relates generally to tabulating machines and particularly to automatic stopping means adapted to be controlled by'any one of a plurality of total taking control "mehcanisms in a tabulator. y

In certain accounting operations carried out on a tabulator it may be desirable to obtain a printed report covering the records of the various departments in a company and also to obtain separate reports covering certain particular departments only. It is necessary, therefore, that the tabulator be momentarily stopped at a pre determined point in its operation in order that a single copy work sheet may be inserted in the 15 machine and also that the machine be again stopped and the sheet withdrawn after the de-' sired information has been printed thereon. To

meet this requirement there has been designed a manually settable automatic stopping device controlled by the total taking mechanism which may be preset to disengage the machine clutch and thus stop the tabulator after a certain predetermined total taking operation.

Cooperating with the stopping device of the invention is certain accumulating and total control mechanism which, briefly considered, comprises three separate accumulating units all situated in the front of the machine and in which the same record items are entered simul- 80 taneously through the medium of Y-wiring in the translator. An automatic total control unit,

the operation of which is initiated upon a change in the designating fields of a card, operates to release the values accumulated in two accumu- 36 lator units while a specially perforated control card is used to release the third unit. Sets of accumulator wheels are also provided at the rear of the machine and under a modified condition of operation, to be described in the body 40 of the specification, are permitted to clear and print their accumulated values. All of the front accumulating units may be released independently of one another so that the machine iscapable of four different operations each productlve of a different total. Under another condition of operation to be described later, all of the front accumulators may be released together to print their respective totals at the same time.

The initiating means for governing the release and retention of the several accumulating units is considered in greater detail further in the specification.

One object of this invention is to increase the flexibility and add to the usefulness of the 56 Powers tabulator by providing a selective automatic stopping means controlled by the total control mechanism, that is variably effective at the will of the operator.

Another object of this invention is to disengage the machine clutch of a tabulator after 5 a predetermined one of several total taking operations by presetting a selective automatic stopping device which will be efiective only in accordance with its setting.

Another object of this invention is a settable m automatic stopping device which cooperates with the total control mechanism and particularly with an operating link of the total control mechanism to transmit the motion of the operating link to the regular tabulator stopping mechanism to disengage the machine clutch.

From the foregoing introduction it may be seen that the mechanism of the invention comprises a variable automatic stopping device which may be preset to cooperate with the regular 20 tabulator stopping mechanism to disengage the machine clutch after a predetermined total operation. The invention is embodied in a tabulator having the usual card feeding, sensing and recording mechanisms common to this type 25 of machine and which is also provided with mechanism for accumulating totals, grand totals, great grand totals and great great grand totals and also control mechanism for effecting the release of said totals automatically and independently of one another.

Other objectsand structural details of the invention will be apparent from the following description when read in connection with the accompanying .drawings, wherein,

Figs. 1 and 2 taken together constitute a right hand view in cross section of the tabulator showing portions of the base mechanisms, the translator and various head mechanisms.

Figs. 3 and 4 taken together constitute a view 40 in exploded isometric of the automatic total and grand total control mechanism in rest position.

Fig. 5 is a view in elevation and partially sectional, taken from the right hand side of the machine showing certain' total control mech- 45 anisms of the machine set in position for automatic Y wire grand total work.

Fig. 6 is a rear view of the translator partially broken away to show the means for raising the naught block.

Fig. 6A is a partial right hand View of the translator as shown in Fig.6.

Figs. 63, 6C, 6D, and 6E are detailed sectional views of certain controlling mechanism mounted on the translator.

' by a picker knife and block 2.

connected by link 3 and arm 4 to a rock shaft Figs. 7 to 13, inclusive, are partial views of the total pull link and certain associated elements inthe various positions they assume during the several total taking strokes.

Fig. 14 is a view in side elevation of the variable automatic stopping device and shows its cooperation with the total control mechanism and the stop shaft of the machine.

Fig. 15 is a front view of the mechanism shown in Fig. 14. I

Fig. 16 is an elevational view taken from the left hand side of the machine and shows the mechanism for engaging and disengaging the machine clutch.

Fig. 17 is a view'showing the two drum like members of the automatic stopping device and the means for positioning the inner drum relatively to the fixed outer drum.

Fig. 18 is a front view of the inscribed casing of the inner drum member of the automatic stopping device.

Figs. 19 to 25, inclusive, are partial views of the total pull link, certain of its associated elements and the actuating lever of the automatic stopping device and are intended to show the relative effective and ineffective positions of the actuating lever for each index position of the stopping device and according to the several lateral pulling positions of the total link.

Fig. 26 is a fragmentary plan view of the base of the machine showing principally the position of the mechanism comprised in the total control unit.

Figs. 2'? to 30 are detail views in side elevation of three cams of the total control unit and their associated linkage.

Figs. 31 to 3'7 are detailed side views of individual elements of the total control unit and their associated mechanism, each view being taken along the respective line indicated in Fig. 26.

G neral description With the improvement and modifications disclosed herein the mechanism of the present invention is applicable to a standard tabulator of the type disclosed in the patents to Lasker No. 2,044,119 and 2,151,406. The mechanism herein described as old is understood to refer to those features and functions of the Powers tabulator which, through public commercial use and frequent formal disclosures, have become well known in the punched card accounting machine fleld.

The tabulator is generally considered as being divided into three cooperating sections or parts. The base section comprising the card feeding, sensing and designating means; the intermediate section comprising a translating or reading transmitting means; the head section comprising in general the printing and computing mechanism.

The mechanism of the base is, for the most part, the same as that disclosed in Patent No. 2,044,119. The exceptional features of the present application, along with the essential base mechanisms, are described below.

A card hopper i (Fig. 1) is provided at the front of the machine and is intended to resolve a pack of perforated record cards which have been suitably arranged for tabulation. The cards may be ejected from the hopper seriatim The block 2 is 6. The shaft 5 is ordinarily rocked once for every cycle of the machine by a cam 6 (Fig. 3) on the main shaft 1. The shaft 1 is motor driven in the usual manner and carries a series of cams appropriately formed and placed to perform their various functions. As shown in Figs. 3 and 4, the cam 6 bears against a follower roller 8 on the arm 9 which is mounted on the shaft H and is connected by a link l2 to an arm [3 fast to the shaft 5. Referring again to Fig. 1, the ejected card is fed between a pair of continually driven feed rollers l4 and I5 and thereby into the sensing chamber l6. The card is held in the sensing chamber by the usual card stop l0 normally actuated, once for each cycle of the machine, by mechanism comprising pivot arm 20, link 30, arm 40 (Figs. 1, 3 and 4), shaft 60, arm 60, link 10, and arm which cooperates with cam on the main shaft 1. The lower pin box I! is moved in vertical reciprocation once for every cycle of the machine by an eccentric strap assembly l8 on the shaft 1. The pins i9, carried by the pin box ll, are urged upwards by springs 2| and are adapted to pass through the perforated plates which comprise the sensing chamber I6. When a card is in the chamber only those pins l9 which are in respective alignment with the perforations in the card will pass through the sensing chamber and be in position to contact and elevate the pins 22 of the upper stationary pin box 23. The pins I9 which encounter no card perforation are ineffective. A positive driving action is given to the elevated effective pins l9 by reason of their cooperation with a locking slide 24. The pins 22 are driven upwards against the tension of springs 25 and are provided with horizontally projecting pins or extrusions 26 and 21. The pins 22 are provided in rows of twelve. Six pins of each row have their extrusions 26 and 21 extending to the right (as viewed from the front of the machine),

, while the extrusions on the other six pins project to the left. The pins 26 on each row of pins 22 coact with a pair of locking slides 28 in the manner illustrated in Fig. l in order that the elevated pins 22 may be locked in their raised position. The locked pins are released near the end of each machine cycle by action of a retract bail 3|, secured between a pair of arms 32 on the shaft 33. By reference to Figs. 3 and 4, it may be seen that cam 34 on the main shaft 1 is so formed as to elevate arm 35 and its associated link 36 once for every rotation of the shaft 1. In its elevated position, link 36 will contact and raise an arm 31 fast to the shaft 33, thereby rotating the shaft 33 and the dependent bail 3| in a counter-clockwise direction, as viewed in Fig.

4 to release the pins 22.

The pins 21 coact with a pair of slides 38 (Figs. 1 and 4) in a manner similar to the cooperation between pins 26 and slides 28 and 23 and impart to them a lateral forward movement. The function of the slides 36 is to initiate an automatic total taking operation through means which will be considered in greater detail further on in the present description. A more detailed discussion of the card feeding and sensing means may be found in the aforementioned Patent No. 2,044,119.

Elevation of the pins 22 will cause a corresponding movement of the wires 4| in the translator 42. As shown in Fig. 1 and Fig. 6 the translator wires ll of the machine end in a joint or cup from each of which extend three separate wires Ma, Mb and H0. Each wire leads into and forms a part of a different translator unit.

In an example shown in Figs. 1 and 2 Bowden wires of a usual construction are used in the translator. Positioned above each wire 4|a, 4|b and He is a spring-pressed pin or interponent ||0 adapted to be moved upward against the tension of its spring I38 to transmit the motion of the Bowden wires to the stop bars hereinafter described.

Positioned in the head of the machine (Fig. 2) and just above each of the translator units is a stop basket 43 comprising numeral stop bars 44 and a normally effective zero stop 45. There are five stops 44 representing, in order from right to left, the odd numerals 1, 3, 5, '1 and 9. To obtain aneven numeral the nine stop is raised and along with it is raised the numeral stop which corresponds to the odd digit which is one lower than the desired even numeral. To illustrate-the numeral four would result from movement of the nine stop bar and the three stop bar.

The heel 46 on the accumulator sector 41 normally contacts the zero stop and when released will swing forward with the type sector 48 to a position determined by a stop 44. Vertical movement of the nine stop bar will dislodge its pin 48 from the notch 5| in the fixed arm 52, thereby permitting the assembly of stop bars 44 of that denomination to move forward an extra space when one of their number has been contacted by the heel 46. If the nine bar alone has been raised there will be, of course, no movement of the other bars 44. The stop basket shown in Fig. 2 is of a conventional type and, in its essential details, is the same as that shown in U. S. Patent to Lasker No. 1,780,621. The zero stop 45 is withdrawn from its restraining position upon the elevation of any of the numeral stops 44 by means of pins 53 on said stops, cam slide 54 and bellcrank 55.

Under certain conditions of machine operation, to be later described, the zero stops of some units 43 will be held upward in effective retaining position by the action of naught blocks, one of which is indicated at 56, slidably mounted at 51 to the translator frame 42.

The type sectors 48 and their associated accumulator sectors 41 are allowed to swing forward under tension of the spring 58 once each machine cycle through the release of bail 59. The printing mechanism comprising hammer 62, type lugs 63 and platen 64 is also shown in part in Fig. 2.

The accumulating mechanism may be the same as that disclosed in the U. S.Patent No. 2,151,406 and comprises front accumulator wheels 65 which may mesh with the accumulator sectors 41 on either their forward or return stroke. Another set of accumulator wheels which are similar in design and function to the wheels 65 are located at the rear of the machine and indicated by the reference numeral 66. Each set of wheels 65 is supported by a pair of arms 61 and is adapted to be put into mesh with the teeth on the sector 41 at a time determined by the movement of arm 68, lever 68a, and its actuating mechanism (not shown), link 1| and arm 12 on thetotal shaft 13.

The rear accumulator wheels 66 are supported by a pair of arms 14 and mesh with racks 15 during a period of the machine cycle determined by timing mechanism comprising, in part, link 16, am 11, shaft 18 and grand total shafts 19 and 8|.

In the ordinary adding operation of the machine the accumulating wheels 65 and 66 are withdrawn from their respective racks 41 and 15 at the start of the cycle. At the beginning of the return stroke of an adding cycle and after the type sectors 48 have reached their farthest forward position the wheels are permitted to move into mesh with their racks and receive a registration determined by the extent of return movement of the type sectors 48. The timing of the accumulator units during total taking cycles is as follows:

On a total operation the front wheels 65 are allowed to remain in mesh with the sectors 41 during the forward stroke of the type sectors 48. The wheels 65 will rotate until they have cleared by reaching zero and after the printing operation will be withdrawn before the sectors 48 begin their return stroke. During this total operation the rear or grand total accumulating wheels 66 are in the non-add position to which they are automatically set upon actuation of shaft 13. All of the wheels 66 will, therefore, retain their accumulation during total strokes.

A grand total is obtained by reversing the above described procedure. On a grand total stroke the type sectors 48 will be governed by the extent of movement of the wheels 66 and the racks 15 as the former are returned to zero. The front wheels 65 are in non-add position during this operation.

The controlling mechanisms operable by the grand total shafts 18 and 8| are not shown herein but are, or may be, the same as those shown in the aforementioned Patent 2,151,406. The shaft 8| is connected directly to the rear accumulator-engaging and disengaging mechanism and, when rocked, serves to alter the timing ofthis mechanism to permit the total to be taken from the wheels 66. The shaft 19 is rocked simultaneously with the shaft 8| and, through means not herein shown causes the front accumulator wheels 65 to remain in a non-add position for the duration of a grand total taking operation. Control shafts corresponding to the shafts 13, 19, and 8|, are shown in Figs. 2 and 19 of Patent 2,151,406 where they are numbered, respectively, 8, 1, and I64. The engaging and disengaging mechanism for the rear accumulator is shown in Fig. 8 of that patent and this figure, in conjunction with Fig. 19 thereof, shows the means whereby the operation of this mechanism is modified, under control of the shaft I64 (8| herein), to cause a total taking operation in the rear accumulator, and under the control of shaft 8 (13 herein) to set the rear accumulator for a non-add operation. Fig. 19 of that patent also shows the means, operable by shaft 8 (13 herein), for setting the front accumulator control mechanism to cause a total taking operation in the front accumulator, and the means operable by shaft 1 (19 herein) for setting this mechanism to cause a non-add operation in the front accumulator.

Total taking control mechanism In Figs. 1, 3 and 4 hereof is illustrated certain automatic total control mechanism for initiating total taking operations upon a change in the designatory matter in a card.

The mechanism shown herein is a modification of the automatic total control means disclosed in the previously cited Patent No. 2,044,119.

As disclosed in the above patent the automatic total control mechanism comprises a normally ineffective control unit adapted to function only during a total taking operation and which is set in motion upon the sensing of a card bearing new designatory matter. As the new designatory matter is sensed certain actuating slides in the sensing chamber cooperate with their associated pre-positioned interponents to trip the total control mechanism to place it under the control of the main shaft and thus initiate a total taking operation. During a total taking operation the control mechanism operates in a series of steps first to disable the card feeding and recording means and to hold the card in the sensing chamber, then to effect a total taking operation and finally to restore the operating mechanism to normal, sense and compute the information contained on the new card and to render the total control unit again ineffective.

In the machine of the cited patent, the result of the above operation is to rock the total shaft 13 connected to the front accumulators of the computing mechanism and cause the printing of a total.

The automatic total control mechanism of this application permits both'a total and a grand total taking operation to be initiated automatically upon a columnar change in the designatory fields of a card. Mechanism additional to that disclosed in Patent No. 2,044,119 has been provided for this purpose while the mechanism of that patent has been modified to cooperate with the new grand total mechanism.

Briefly stated the present automatic total and grand total control unit may be considered as comprising two totaling mechanisms, each having individual tripping means. One portion of the control mechanism is similar in function and operation to the mechanism of the abovementioned patent and operates to secure the usual group total. The additional or grand total mechanism operates to effect two successive operations of the group total mechanism, during the second of which an operating link of the total control mechanism is shifted to initiate a grand total taking operation.

Therefore, it may be seen that group total taking operations may be accomplished independently of the grand total mechanism and that a grand total operation must first be preceded by a total operation.

The change-of-designation necessary to bring about these operations may occur in a minor designating field on the card, and this causes a group total taking operation, or it may occur in a major designating field and cause a grand total taking operation which will automatically be preceded by a total operation.

The following is a more detailed discussion of the automatic total control mechanism in its new form including the means for tripping said mechanism upon a change in designation.

Referring now to Figs. 1 and 4 it may be seen that located above and in front of the upper pinbox 23 is a series of hand settable positioning members 83 formed as illustrated therein and equal in number to the slides 38. Each member 83 has 2. depending interponent 84, the head 85 of which may be interposed between either of two bail rods 86 or 81 and the nose 88 of a change-of-designation slide 38. All of the members 83 are adapted for manual movement, whereby they may be positioned in any of three vertical positions. The cooperation of notches 89 in the members 83 with a retaining spring 9| serves to hold the members in their set positions. In its highest, or ineffective, position, the head 85 of the interponent 84 is raised out of the path of movement of slide 38 and thus is unable to rock either bail rod 86 or 81. In its second position, indicated at 83a in Fig. 4, the interponent head 85 lies between slide 38 and the upper bail rod 86.

In its third position, indicated at 831), the interponent head 85 lies between the nose 88 of the slide 38 and the lower bail rod 81. The bail rod 86 extends between a pair of arms 92 while the rod 81 is supported by a somewhat similar pair of arms 93. The arms 92 and 93 are fast to their respective shafts 94 and 95. As shown in Fig. 4 the lower part of each arm 93 has a recess or cutout portion, the inner edge of which bears against the bail rod 86. From the shape of arms 93 and the relative position of interponent 84, bail rod 86 and 81 and nose 88, it will be seen that in accordance with the setting of an interponent 84, its associated control slide 38 may be entirely ineffective, or it may cause the rocking of bail rod 86 alone, and hence shaft 94, or it may cause the rocking of bail rods 81 and 86 together as well as their respective shafts 95 and 94. The bail rod 86 may thus be rocked alone Whereas the rocking of bail rod 81 is accompanied by a simultaneous rocking of bail rod 86.

Referring to Figs. 3 and 26, the mechanism for controlling group total operations, comprises in part a three tooth ratchet 96 secured to a shaft 91 (see also Fig. 33), an actuating pawl 98 therefor and a pawl lever 99. This pawl lever is actuated by cam I8I on the main shaft 1, and one branch I82 of the forked push rod I83, upon disengagement of the trip latch I84 which normally engages the rear extension of lever 99 and holds it ineffective. The latch I84 is tripped upon a change in either the minor or major designating field through slide 38, interponent 84, shaft 94 and arm I85 thereon.

The controlling mechanism further comprises the six tooth rachet I86 (see also Fig. 31) also secured to the shaft 91. This ratchet I86 has three pairs of teeth, with a blank space corresponding to a missing tooth between each pair of teeth. The ratchet 96 is a three toothed wheel with a blank space corresponding to a pair of missing teeth between each two teeth. Therefore, one tooth of ratchet 96 and one pair of teeth of ratchet I86 are complementary to each other so that the two ratchets, taken together, operate as a single 9 tooth Wheel. The ratchet wheel I86 is actuated by pawl I81, pawl lever I08, push rod I89 and cam III on the main shaft 1.

In the rest position of the group total control mechanism the two pawls I81 and 98 are unable to engage the teeth on their respective ratchet wheels I86 and 96 since the pawl I81 slides ineffectively in the blank space on wheel I86 and pawl 98 is held upward by trip latch I84. When, however, the ratchet 96 is advanced one step as a result of the tripping action instituted by control slide 38, ratchet I86 is advanced towards the end of the main shaft revolution and about 338 degrees in phase after the actuation of ratchet 96. Fastened to the shaft 91 are a detent cam II2 (see also Fig. 35), the purpose of which will be described later, and the cam II3 (see also Fig. 27) for operating the retract bail 3| through the arm II4 secured to the shaft 33 Cam II3 also serves to actuate the card stop I8 through arm II (see also Fig. 29) secured to the shaft 58. Also fast to the shaft 91 is cam II6 (see also Fig. 30) for controlling the total link I", the

cam II 8 (see also Fig. 28) for suspending the twice during a total taking operation; first, during the second step of ratchet wheel I06 and, again, during the third step of the ratchet. Between the second and third steps of movement of the ratchet wheel I06 an artificial change of designation (later to be described) occurs and the arm I22 is rocked downward only to be raised again as the ratchet moves through its third step. This third step of movement of ratchet I06 is, as will be later described, the normalizingstroke of the total control unit and occurs at a time when the pins 22 are in their highest elevated position. The control slides 38 are thus restored during this normalizing stroke Y and will not again be actuated until the next computing cycles.

change of designation occurs.

The components of the additional or grand total mechanism are fastened together'and secured to a sleeve loosely mounted on the shaft 91. A part of this additional mechanism is the ratchet I23 (see also Fig-32), constructed as an eight tooth wheel and actuated by pawl I24 on the pawl lever I25. This pawl lever is actuated by cam IN on the main shaft 1 and the other branch I20 of push rod I03. Pawl lever I25 is raised simultaneously with lever 99 when the trip latch I26 is released by anti I2] onthe shaft- 95. The shaft 95 is rocked only upon a change in the major designating field of the card.

The additional mechanism further comprises cam I28 (see also Fig. 37), which at the beginning of the third stroke of ratchet I23, and by means of cam follower I29 on the arm I3I shifts the total link III to grand total position and at the end of, the fourth stroke permits it to assume its normal total position. Further mechanism necessary to accomplish this movement is shown in Fig. and will be described later in the speciflcation.

The additional mechanism further comprises a detent cam I32 (see also Fig. 34), one purpose of which is to position the ratchet I23. The cam I32 is provided with eight notches, two deeper ones diametrically arranged for the rest position of the cam, i. e., during regular Intermediary to these deeper notches are arranged three shallower notches corresponding to the three. working steps of ratchet I23. Cooperating with the cam I32 is a roller I33 mounted at one end of the lever I34. The lever I34 has rearward extensions I35 and I36. The extension I35 is adapted to cooperate with pin I31 on the grand total trip latch I26 and with the stud I39 on the retaining latch I4I, while extension I3'6 cooperates with pin I42 on the total trip latch I04 and with stud I43 on the retaining latch I44. The extensions I35 and I36 are normally inefiective for cooperation with the above described mechanisms since the roller hold the trip and retaining latches ineffective to engage the pawl arms 99 and I25. Therefore, ratchets 96 and I23 will be advanced by cam IOI, through pawls 98 and I24, during the second, third and fourth position of cam I32.

The retaining latches I4I and I44 are normally blocked from engaging their respective pawl levers I25 and 99. A lever I45 has a roller I46 at one end which follows the periphery of cam N2 of the intermediate mechanism. The lever I45 is formed with a downwardly extending arm I41 carrying a laterally projecting stud I 48 which extends across the front of the retaining latches I44 and MI. The cam II2 has three notches corresponding to the rest positions of the mechanism and to those transitory positions in which a group total taking operation is changed over to a grand totaling operation. When roller I46 lies in a notch of the cam II2, latches I44 and MI are held ineffective by stud I48. When the roller I46 is forced out of the notch and onto the raised part of cam II2, stud I48 will pivot clockwise and allow latches HI and I 44 to follow this clockwise motion by means of springs I49, until they latch over their respective pawl levers I25 and 99.

This release of the retaining latches occurs immediately after the first step of the group total control mechanism and is utilized to prevent actuation of the pawl arms 99 and I25 during the subsequent steps of the control mechanism or until the trip latches I04 and I2'6 return to their laching position. The artificial change of designation produced by the rising and falling pins of the sensing box while the card is locked in the chamber during a total taking operation is thereby rendered ineffective to release the lever 99 and institute another and undesired total taking operation. It has been seen that the retaining latches I44 and MI are disabled during grand total cycles in order to permit two successive operations of the group total control mechanism.

A columnar change in the minor designatory field of a card institutes a total taking operation in the following manner: In Fig. 4 the interponent 83a is shown as set to rock the group total bail 86 upon actuation of the minor designatory slide 38. As the slide is moved by the elevation of a new pin 22, the bail 86 is rocked, thereby rotating the shaft 94 counter-clockwise to trip the latch I04 through an arm I05. The pawl lever 99 will, of course, drop and ratchet 96 will be advanced one step as soon as cam IOI raises the push rod I03. The' stepping of ratchet 96 will advance cam II3 to disable the locking slides 28, through arm II4, shaft 33 and bail 3I, and to lower the card stop I0, through arm II5 on the shaft 50, cam II8 to disable the card feed mechanism, and advance cam II6 within one step of actuating the total link III. Cam H2 is likewise rotated one step to render effective the retaining latches I44 and HI. 330 degrees of rotation after the actuation of pawl lever 99, push rod I09 will raise pawl lever I08 to advance the total control mechanism a further step. The cams H8, H6 and H3 are advanced a second step also and a total operation is effected by the downward pulling motion of total link III in a manner later to be described. After a full rotation of shaft I, cam III will again elevate push rod I09 to advance ratchet I06 a third step to return the group total control mechanism to normal. 

